Printing telegraph



Oct. 25, 1932. H.L. KRUM PRINTING TELEGRAPH Filed Jan. 27. 1930 0 Sheets-Sheet 1 Oct. 25, 1932. H. KRUM PRINTING TELEGRAPH 10 Sheets-Sheet 2 Filed Jan. 2'7, 1930 & I imgl Oct. 25, 1932. H, K M 1,884,754

PRINTING TELEGRAPH Filed Jan. 27, 1930 10 Sheets-Sheet 3 INVENTOR fill era Z Jwwzz ATTOR Oct. 25, 1932. H. KRUM PRINTING TELEGRAPH Filed Jan. 27. 1930 10 Sheets-Sheet INVENTOR H z/ j/ ATTORNEYS Oct; 25, 1932. H. L. KRUM PRINTING TELEGRAPH Filed Jan. 27, 1930 n. m n l IN V EN TOR.

10 Sheets-Sheet 5 2/ ATTORNEJ Oct. 25, 1932. H. 1.. KRUM PRINTING TELEGRAPH Filed Jan. 27, 1930 10 Sheets-Sheet 6 9/ W1 ATTORNEY Oct. 25, 1932. H. L. KRUM 1,884,754

PRINTING TELEGRAPH Filed Jan. 27. 1930 1Q Sheets-Sheet 7 mg! ATTORNEY Oct. 25, 1932. KRUM 7 1,884,754

PRINTING TELEGRAPH Filed Jan. 27, 1930' 10 Sheets-Sheet 8 INVENTOR jf/olrwazfl/"w/iz BY WkWa ATTORN EYS 0a. 25, 1932. H. L. KRUM 1,884,754

' PRINTING TELEGRAPH Filed Jan. 27, 1930 1Q Sheets-Sheet 9 2? iii? if? ATTORNEYS Oct. 25, 1932. H. 1.. KRUM 1,884,754

PRINTING TELEGRAPH Filed Jan. 27, 1930 10 Sheets-Sheet 1O D B w fi limzzz%%m ATTORNEYJ' Patented 0a. 25, 1932 v UNITED STATES PATENT OFFICE- HOWABD L. KRUI, OF CHICAGO, ILLINOIS, ASSIGNOR TO TELE'IYPE CORPORATION, OF CHIGAGO, ILLINOIS, A CORPORATION OF DELAWARE PRINTING TELEGRAPH Application filed January 27, 1930. Serial No. 423,781.

My present invention relates to selecting and recording mechanisms and is especially suitable for printing telegraphs particularly of a bulletin painting type, but is also equally applicable to various other types of selective register devices.

Bulletin printing or broad tape printers are usually employed as news printers in offices, where comparative quietness ofoperation is very desirable. Accordingly an object of my invention is to provide a telegraph printer with cushioning devices to minimize the noise of printing operations.

Devices of the character here involved generally include a printing platen which carries the paper or other material upon which the printing is to be accomplished, a printing mechanism for the impression of the desired character on the paper and a selecting mechanism which controls the printing mechanism. Another object of my invention a is to provide novel means for shifting the type carrying means for letter spacing with respect to a paper platen and at the same time maintain it at all times in operative relation with the selecting mechanism.

Although it is usually desirable to operate atransmitter and printer in combination,

conditions may arise where it is desirable to operate the transmitter or the printer alone. Accordingly, a further object of my invention is to providemeans in a device of the above character for arranging the keyboard and sender as a detachable unit from the printer and vice versa, so that they may be used singly in certain limits in a line of printing for automatically returning the carriage and for line feeding in addition to a normal carriage return operative in response to redetermined code combinations of impu se conditions whereby a page printer may be operated on tape printer signals.

Another object of my invention is to provide a novel simplified typewheel printer in which a paper platen is movable with respect to the typewheel for printing operations.

In printers of this character, in order to provide for high speed operation, it is desirable that the line. magnet be required to perform a minimum of work. To this end, provision is made in the present device for operating the magnet as a relay by leaving its armature free to move between its two limits without performing any work.

Further objects of my invention are to provide a simplified printing device in which receiver may comprise a selecting mechanism and a novel typewheel adjusting mechanism for bringing the type faces into operative position, novel spring operated impresslng mechanism for bringing the printing platen into printing relation with a selected type face, novel s acing mechanism for shifting the typewhee carriage along the line of printing, novel case shift mechanism for changing the relation of the typewheel with respect .to the platen, novel normal and automatic carriage returns, a novel paper feed, and novel cushioning means for preventing noise by printing operations.

Still a further object of m invention is to provide a novel printing mechanism in which all of the functions or stunt operations of the printer are controlled b the same selecting mechanism which contro s the selection of the type face for printing. ,7

A further object of my invention is to provide an interchangeable function control member whereby a machine of the type here'- in disclosed may be readily modified to .per-

form various functions.

Another object is to provide a case shift mechanism adapted to operate in responseto a full code combination of impulse conditions.

Still another object is to provide means for mil ' ers being a home recorder for-the transmita1 view showin ter.

Figure 3 is a front elevational view of the preferred embodiment of my invention partially in elevation and partially in section.

Figure 4 is an edge elevational view of one of the friction clutch units embodied in my invention.

Figure 5 is a fragmentary vertical sectiondetails of the flutter cam and flutter lever em odied in the invention.

F igure 6 is a fra entary elevational view showing the end 0 the armature and the operating end of the bell crank as embodied in the present invention.

Flgure 7 is a view similar to Figure 6 showing the elements of Figure 6 in an alternative position.

Figure. 8 is a vertical sectional view with some Iparts in elevation, particularly disclosing t e orientation device, as embodied in the invention.

Fi re 9 is a fragmentary elevational view showing the combination clutch embodied in the resent invention.

Figure 10 is a vertical sectional view with some parts in elevation showing the combination clutch andv the stop means associated therewith.

Figure 11 is an enlarged detailview dis- I closing-the pin barrel, signal levers and stop and partly arm, as embodied in the invention.

-Figure 12 1s a vertlcal sectional v1ew discloslng the signal receiving, recording, transferring and indexing mechanism, as embodied in the invention.

Figure 13 is a fragmentary view partially in section and partially in elevation particularly disclosing the index stop arm embodied in the invention. I

Figure 14 is a broken top edge view of the mechanism shown in Figure 13.

Figure 15 is a detail view partly in section in elevation showing the caseshift jockey. r

Figure 16 is an elevational view partially in section showing the case-shift transfer mechanism embodied in the invention.

Figure 17 is a vertical sectional view particularly disclosing the carriage, the typewheel and the case-shift mechanism embodied in the invention.

Figure 18 is a detail view disclosing the typewheel lock.

Figure 19 is a detail .view showing the arm for case-shifting the typewheel.

Figure 20 is a detail sectional view, partly in elevation, showing details of, mechanism for performing the printing operation, the paper feed operation, and the carriage return.

Figure 21 is a detail elevational view showing the interference devices for effecting the return of the carriage.

Figure 22 is a detail view disclosing the carriage return sto and latch means.

' Figure 23 is anot er detail view of the ap paratus of Figure 22, as seen atv right angles thereto.

Figure 24 is a detail view partly in section and partly in elevation, particularly disclosing the trip bail embodied in the invention.

Figure 25 is a sectional view, taken on the line 25.25 of Figure 35, showing details of modified carriage return and line feed mechanism.

Figure 26 is a detail View showing one of the testing members of Figure 25.

Figure 27 is a sectional view, taken on the line 2727 of Figure 35, showing details of a modified print-suppression mechanism.

Figure 28 is a detail view of the assembly of the adjusting screw of Figure 27.

Figure 29 is a detailed view of the stud member of Figure 35 showing the assembly of its parts.

Figure 30 is a detail view of the adjustable stud of Figure 25 and shows the assembly of the stud and associated structural elements. l

Figure 31 is an elevational view showing a modified construction of presser rolls and paper knife.

Figure 32 is a side elevational view of the mechanism of Figure 31, partially in section, taken on the line 32-32 of Figure 31.

Figure 33 is a sectional view, taken on the line 3333 of Figure showing details of a modified ease shift mechanism.

Figure 34 is a detail view of a modified pin barrel having five pairs of ins and suitable for use with the case shi t mechanism of Figure 33. I

Figure 35 is a plan view showing the right end of the square stop shaft with the modified arrangement of the rotary abutment members and five testing elements.

Figure 36 is av fragmentary front elevational view showin a part of the mechanism of Figure 3, modi ed to include means for effecting space suppression.

. Figure 37 is a longitudinal sectional v1ew through the shaft, journal and rotary abutments of Figure 35, showin the manner of assembling the parts t-hereo Figures 38 and 39 are detail Views of modified rotary abutment units.

Figures 40 and 41 are detail views showmg mechanism for adjusting the height of the motor shaft.

Figure 42 is a detail view of one of the posts shown in Figures 40 and 41.

Figure 43 is an elevational view partially in section showing a modified elevator mechanism for the typewheel.

Figure 44 is a detail view of the mechanism of Figure 43 showing the articulation of the typewheel shaft with the elevator slide.

Figure 45 is a plan view showing details of the mechanism for mounting the ink roller.

Figure 46 is an elevational view showing further details of the mechanism of Figure 45 and illustrating the ready replacement feature of the ink roller.

Figure 47 is a detail view of the ink guard shown in Figure 43.

The keyboard and sender In Figure 1, thekeyboard and sender which may correspond in all fundamental details to the keyboard andsender disclosed in the U. S. Patent 1,595,472, issued to me, August 10th, 1926, comprises a cast metal base or frame 10 provided at the front thereof with a keyboard 11. Extending vertically from the base 10 and secured thereto by means of screws 12 are a pair of uprights 13 which support a shaft 14 therebetween as shown in Figure 20. Loosely mounted on the shaft 14 is a cam drum 15 which is provided with a series of cam slots 16. As the cam drum 15 is rotated, the slots 16 successively cooperate with a set of switch controllers (not shown) and as described in the above mentioned patent control the transmissionof code combinations of impulse conditions in accordance with the keys operated. The cam drum 15 has at one end thereof a slot 17 which embraces an extension 18 on a sleeve member 19 loosely mounted on the shaft 14 adjacent the cam drum 15. The connection between cam drum 15 and the sleeve member 19 is such that the two members 15 and 19 rotate together but sleeve member 19 may slide longitudinally with respect to the shaft 14. The sleeve member-19 is provided with teeth 20 which are adapted to cooperate with teeth 21 on a gear 22 which is fixed to the shaft 14. The gear 22 meshes with a spiral gear 23 which is fixed to the main shaft 24 of the printer and which is driven continuously at uniform speed by the motor 25, (Figure 1) of'the printer. I As described in the above mentioned patent, the member 19 is normally disengaged from gear 22 and accordingly does not rotate. On the operation of any key lever member 19 is moved longitudinally to engage the teeth thereof with the teeth of gears22 and cam drum 15 is thereupon driven through one revolution to transmit the code combination of impulse conditions in accordance with the operated key.

Figure 2 is a diagram of preferred electrical connections employed in my system. The transmitter contact arms 26 are connected together and to battery and through a sending relay 28 to ground. As will be understood, contacts 26 and their adjacent contacts 27 engage in various combinations under control of drum 15 and the operated key. The armature 29 of the relay 28 cooperates with contact 30 or contact 31 to extend positive or negative battery over a line 32. This line may include a home station polar magnet 33 and extend to a mid-line station polar magnet 34 and a terminal station polar magnet 35. A resistance 36 is included in the connection .between positive battery and contact 30 and a similar resistance 37 is included in the connection between negative battery and contact 31. The operating circuit extends from positive (or negative) battery through resistance 36 (or 37) contact 30 (or 31), armature 29, polar magnet 33, line 32, polar magnet 34, line 32 and polar magnet to ground. The system thus is organized to transmit from the contacts 26, 27 for variably operating the Signaling receiving and storing Motor 25 (Figure 1) drives a shaft 38 (Figure 3) which has secured thereto a spiral gear 39. In mesh with the spiral gear 39 is a spiral gear 40 on the main shaft 24 which is journaled in bearings 41 and 42. Mounted on the main shaft 24 and fixed thereto by means of a pin 43 is a friction clutch unit 44,-

the purpose of which will appear hereinafter. In abutting relationship with the clutch 44, is the sleeve member 45 having a flange 46 to which the gear 40, which drives the shaft 24, is secured by means of screws 47. The sleeve 45 is keyed into the key way 48 to prevent it from turning on the shaft 24. The journal member or inner ball race 49 of the bearing 41 fits closely upon the shaft 24 and abuts the sleeve 45 and is keyed into the key way 48. A friction'clutch unit 50, to be described in detail hereinafter, fits closely upon the shaft 24 and abuts the race 49 and is also keyed into the key way 48. From a point within the clutch 50, the shaft 24 has an extension of reduced diameter as shown at 51. A sleeve 52 surrounds the extension 51 and loosely mounted on this sleeve is a hollow two forms of motion; namely, rotation about its longitudinal axis and reciprocation along said axis. The manner in which the pin barrel 53 is operated and the purpose thereof will appear fully in the following description.

Adjacent the sleeve 52 on the shaft 24 is a washer 54 which is of larger diameter than the sleeve 52 for retaining the pin barrel 53 upon the sleeve 52 and also forming a stop for the pin barrel 53 against which the pin barrel is pressed as will be described. A nut 55 upon the shaft 24 clamps all of the elements 52, 54, 50, 49 and against the clutch 44 and all of these elements are rigidly secured to the shaft 24 so as to rotate therewith.

The friction clutch (see Figures 3 and 4) is an integral removable unit and comprises a flanged sleeve member 56 as one operating.

element and a riven disc 57as the other operating element. The driven disc 57 is rotatably mounted upon ,the sleeve 56, as shown most clearly'in Figure 3. In addition, a

.friction plate 58 is loosely mounted on the member 56. A friction member 59, such as a felt washer, is placed between plate58 and driven disc 57 and another friction member 59 is placed between the disc 57 and the flangeof the member 56. The friction members are threaded member 60 and its lock nut 61.

friction members are pressed. into engageconfined upon the member 56 by an adjustable The ment with the members 56, 57 and 58 by an annular member 61' comprising a ring with a plurality of radial wings turned alternatelyright and left. The wings engage corrugations in the threaded member 60 and the loose friction plate 58 and cause the friction plate 58 to turn at all times with the principal operating member 56 while at the same time pressing the friction elements together. The tension of the clutch is adjustable by means of the threaded member 60 and its lock nut 61.

The driven member 57 of the clutch 50 has a contour as shown in Figure 8. By reason of its shape member 57 functions as a cam to operate a bail 62 which has a roller 63 in continuous engagement with the periphery of member 57. The purpose of bail 62 will appear hereinafter. The disc 57 is provided with a slot 64 into which extends the arm 65 of the pin barrel 53 as shown in Figure 3. The arm 65 is positioned within the slot 64 at the time that the pin barrel is assembled upon the sleeve 52.' When the pin barrel 53 is not restrained the disc 57, through this slot and arm connection, drives the pin barrel 53.

As shown in Figures 3 and 8, an adj ustable orientation arc 66 is provided adjacent the' .clutch 50. Projecting laterally from the orientation are 66 is a stop arm 67 adapted to be engaged by arm 65 of the pin barrel for stopping the rotation of the pin barrel. The lengths of the stop arms 65' and 67 are -such that they engage to stop the pin barrel 53 when the pin barrel is at the right hand of its limited travel upon the sleeve 52 but they clear each other and permit the pin barrel 53 to rotate when the pin barrel is at the left hand of its limited travel upon the sleeve 52.

The angular position in which the pin barrel is stopped is determined by'the position of the stop arm 67 which is adjustable by means of the are 66 sliding upon its guide studs 68 and 69 and operated by its handle 70. When adjusted it is locked by the nut 71 on the loose stud 69. j

The selective operation of the pin barrel 53 as it is rotated is controlled by asingle selector magnet which may be of any well known construction. As shown in Figure 12, the selector magnet 33 is of a sensitive polarized type such as used in stock ticker operation and comprises a permanent U-shaped magnet 72, surrounding the pole pieces 73. Disposed within the pole pieces 73 are the magnet windings 74 which are energized in accordance with impulses received over the .gizesin accordance with marking and spacing impulsbs received over the signalling line 32, the extension 77 of armature is moved into and outofthe path of a bell crank lever 79 shown in detail in Figures 6 and 7. The bell crank lever 79 isrpivotally mounted at 80 on a stationary part'of the frame work of the machine as shown inFigure 3. One end 81 of the bell crank lever 79 is formed and positioned to engage the end 77 of the armature 75. .The mutual relation of ends 77 and 81 is such that when the armature 75. is in the position shown in Figure 7, the end 77 prevents motion of the bell crankend 81. The other end 82 of the bell crank is forked to span the operating end 83 of a flutter lever'84. The flutter lever 84 is pivotally mounted on a pin 85 and has a pair of arms or cam followers 86 and 87. s

In operative relationwith the cam followers 86 and 87 is the flutter cam 88, which is secured tothe pin barrel 53. The flutter cam- 88 has a plurality of radially arranged right and left corrugations or flutes such as 89 and.

"-9 in either operated position until the impulses marking pin and a spacing pin. Associated with each pair of selector pins 94 is one of six selector levers 95, Figure 12, pivotally mounted .on a common rod 96 suitably carried by the frame of the machine. A common stop rod 97 extends through all of the selector levers and limits the angular rotation of the levers around their pivot 96. Each selector lever 95 has two operating cam arms, the

upper or marking cam arm 98 and the lower or spacing cam arm 99 the one or the other of which is engaged by its associated selector pin 94 as it rotates past the lever. The ends of the cam arms 98 and 99 are off-set with respect to each other so that when the marking pin individual to a particular selector lever lines up with the cam arm 98, the other cam arm 99 will freely pass by the spacing pin individualthereto. When the spacing pin is in line with the cam arm 99, the marking pin will freely pass by the cam arm 98. In ad dition the selector levers 95 each have two abutment arms, the right or marking abutment arm 100 and the left or spacing abutment arm'101.

p The selector levers95 are carried in a selec tor lever guide unit 102. The selector levers 95 have no normal position, but remain set in a succeeding code are such as to shift them to the opposite position. Inasmuch as they have no normal position, very little power is necessary to operate them andthe number I of operations is reducedas they do not operate until a change in the code signal is received,

In order to insure against accidental movement of the selector levers from the position to which. they have been tion of impulse conditions is as follows :v

The normal condition of idleness or stop between code combinations of impulse condi tions is produced by a marking pulse of current. This marking pulse energizes magnet 33 and lifts the armature 75 bringing the operating end 77, into the position shown in Figure 7, thus holding the bell crank 79 in the position shown, with the ends81 and 82 moved, a latch-' 11g means 18 PIOVldd for each of the selector in their back or marking position. The forked end 82 of the bell crank 79 restrains the end 83 of the flutter lever 84, thus holdin the flutter lever in its marking position wit the cam followers 86 and 87 moved to the right. The cam followers 86 and 87 being held fixed, it follows that as the flutter cam 88 turns, the flutter cam 88 and pin barrel 53 must move laterally by sliding upon the sleeve 52. When the stop arm reaches that angular position in which it may engage the stop pin 67 the flutter cam 88 will have a left flute within the followers 86 and 87, the pin barrel will be in its right hand position, as shown in Figure 3, the arm 65 and thearm 67 will engage as shown in the figure and the pin barrel will be stopped and the friction clutch 50 will slip its friction members. This is the normal condition of idleness or the position of stop between codes, awaiting the ensuing start signal or spacing signal in the line 32 and coils 74 of the magnet 33.

The sender (Figure 2) now sends a start-' ing impulse, which is always negative, followed by six other impulses, each of which is arbitrarily either negative or positive. The negative starting impulse moves the armature 7 5' downward, Figure 7, and the operating end 77 releases the bell crank end 81 as shown forward as shown in dotted lines in Figure 6 and the camfollowers 86 and 87 span a left flute 90, Figure 5. The niotor 25 drives the pin barrel 53 and flutter cam-88, and a right flute 106 of the flutter cam 88 passes between the cam followersl86 and 87. The bell crank lever 79 is rocked clockwise as viewed in Figure 6, from the position shown in dotted lines to the position shown in full lines.

Should the first signal pulse be marking, the armature 75 will move its end 77 into the 'path of the end 81 as shown in Figure 7. As

the motor rotates the pin barrel 53 and the flutter cam 88, the left flute 107 of the flutter cam 88 passes between the cam followers 86 and 87. These are now immovable'because of the obstruction by the end 77 of the arma ture 75 and consequently the pin barrel 53.

moves to the right against the tension of the spring 93. In moving to the right, .the

pin barrel 53 carries the marking pin108, Figure 11, into alignment with the marking cam 98 of the first selector lever 95 and carries the spacing pin 109 out of alignment with the spacing cam 99 of the first selector lever 95, as shown in Figure 11. As the pin barrel continues turning, the pin 108 passes under the cam 98. If the first selector lever is already in its upper or operated position, the pin 108 has no effect on 1t. But, if this lever is not in its upper position pin 108, acting on cam 98, forces the lever up into that position. The spacing pin 109 passes beside the spacing cam 99 without engaging the spacing cam because it is out of alignment.

Had the first signal impulse been a spacing condition, the armature 75 would not have moved, the bell crank 79 would have remained unrestrained, the left flute 107 would have moved the flutter-lever "instead of moving the pin barrel, the markin pin 108 would have remained out of the pat of the marking cam 98 of the first selector lever and. the spacing pin 109 would have remained in the path of the spacing cam 99 of the first selector lever, and as the pin barrel rotated the pin 109 would have engaged the spacing cam 99 .and would have shifted the first selector lever 95 into its alternative position.

I impulse is marking ormoves the flutter lever if the impulse is spacing. The second marking pin 111 on the pin barrel 53 then operates the marking cam 98 of the second selector lever 95 if the pin barrel has been shifted to the right or its dotted companion operates the spacing cam 99 of the second selector lever 95 if the pin barrel has not been shifted. This operation is repeated for the remaining four impulses and then the marking stop impulse moves the armature end 77 into the I path of theend 81 of the bell crank 79 and the pin barrel 53 is shifted to the right, the stop arm engages the stop arm 67 and the pin barrel53 stops. This operation effects the positioning of the six selector levers in accordance with the six impulses received over the line 32.

' As will be clear to those skilled in the art, all of the movements of the pin barrel 53 are accomplished substantially entirely by power supplied by the motor 25 driving the pin bar-' re .that is, not only is the power for rotating the pin barrel 53 supplied-from this original source, but due to the shaping of the "flutter cam 88;"the rotative motion is translated into a linear motion for moving the pin barrel 53 to the right or left, although this movement is controlled by the line magnet. Except, therefore, for releasing the clutch 50 in'response to a start impulse there is a mini- .chronism with the speed of code mum requirement of power from the line- The receiving line magnet 33 may therefore be of a very delicate structure responsive to very small currents and having a minimum of inertia and may therefore operate at very high speed. Inasmuch as the localsource of power supply may be of any value within practical limits, the pin barrel 53 may rotate and move longitudinally at a very high speed. It will, of course, be understood that the pin barrel is rotated at a speed which is in synimpulsing by any well known means.

Transfer-flag and indewing transfer lever 112 is controlled by its companion selector lever 95 through the engagement of one or the other of its two arms 113, 114 with one or the other of the two abutments 100 and 101 of the selector lever 95. All of the transfer levers 112 are carried by a pivot shaft 116 which is in turn carried by a transfer bail 117. The transfer bail 117 is mounted upon the transfer bail shaft 118 and is operated by a main cam 119 which is mounted to turn freely on the main shaft 24 (see Figures 3, 9, 10 and 17) The main cam 119 is provided with a cam groove 120 and an-external cam edge 121 and is driven by the friction clutch 44 and by a toothed clutch 122 acting co-operatively. The friction clutch 44 issimilar to the friction clutch 50 and comprises a flanged sleeve member 123, a driven disc 124 having a lug 125 and an adjusting member 126. A pin 127 (Figure 10) fixed to the main cam 119 engages the s de of the lug 125 in the disc 124. Accordingly, when the disc 124 rotates, it drives the mam cam 119. 1

When the motor 25 is operating and line signals are not being received, the main cam 119 is prevented from rotating. This is effected by end 128 of the trip bail 62, which at such times engages the lug 125 of the driven disc 124, as shown in Figure 10, and thereby causes the clutch 44 to slip its friction members. The trip bail 62 is supported pivotally upon the. rod 129 and a spring 130 (Figure 24) normally urges the operating end 128 of the bail 62 away from the driven disc 124 and urges its operated end carrying roller 63 against the cam edge of the driven disc 57. When a portion of the driven disc 57 having a reduced radius passes under the roller 63, the bail 62 rocks on its shaft 129 and the operating end 128 of the bail 62 leaves the lug 125 of the driven disc 124, perthe fixed abutment 135.

132 at all times engages the main cam 119' and. cam follower roller 138 mitting the disc 124 to rotate. As disc 124 rotates it operates main earn 119.

The main cam 119 may be driven also by the toothed clutch 122 (see Fig.9). The clutch 122 comprises a driving member 131 which is secured upon the main shaft 24 and a driven member 132 which is sleeved upon the main shaft 24. The sleeve member 132 is urged towards the right at all times by the spring 133 but when in its position of rest it is forced to the left by engagement of the annular crown cam 134 thereon with The sleeve member by means of apair of spline teeth 136 which always engage the sides of a diametrical groove in the hub of the main cam 119. When the sleeve member 132 is permitted to occupy its right hand position it, engages the driving member 131 and transmits the power of the main shaft 24 through nonslipping members to'the main cam 119. The spring 133 operates incidentally to press the main cam 119 against the flange123 of the clutch 44. Since the flange 123 is at all times turning and the main cam 119 is at times stopped, an antifriction' member or washer 137 is interposed. The main cam 119 by its cam groove 120 (Figure 17) moves the transfer bail 117 to depress the pivot shaft 116 (Figure 12) to move the transfer levers 112 at the proper instant in the cycle of operation.

The signal index mechanism comprises five selector discs 139 mounted to turn through a limitedangle as loose sleeves upon a' fixed tubular support 140 (see Figure 12). Each selector disc 139 is controlled by a transfer lever 112 whose head member 115 engages the sides of a radial slot 141 in the selector disc 139. At right angles to and equally spaced around the circumference of the selector discs 139 and guided in slots in three radially slotted guide plates 142 are a series of index pins 143 provided with cam rollers 144 (see Figure 3). The index pins 143 are supported in an arrangement in which each is parallel to all others and in which the A guide plates 142 'total assembly is cylindrical. Each index pin is pivoted upon a circular pivot plate 145. A notch in each of the index pins engages-the edge of the ivot late 145 as shown at 146 and prevents t e indhx pin from moving end-wise. A toroidal radially contractible pivot spring .147 holds all of the index pins against the pivot plate 145. The three prevent, the index pins from moving along the arc of the cylindrical assembly. The motion of each index pin occurs at the end of the pin remote from the pivot plate 145 andis in a direction radial to the axis of the cylindrical assembly and IS COl'ltI'OllBd by two elements.

"The first control element for the index pins is a spring for operating the free end of the index pins towards the axis of the c lindrlcal assembly. A convenient form o spring 1 system is shown in, which each Index pmis engaged by a toroidal spring at a median point of each index pin. The index pins,

are bentin two shapes and are assembled by using the two shapes alternately. Two.

cumferential edges according to code in such manner that at all times a notch in each disc will be in alignment with a notch in each of the other discs and a single specific index pin will be permitted .to drop into the aligned notches and move toward the axis of the cylindrical system. Thus in Figures 3 and 12,

the reference numeral 150 indicates a pin which has dropped into aligned notches in the discs. See also the pin designated by numeral 151 in Figure 13. For each setting of the selector discs 139 one of the index pins 143 will have under it five notches in alignment (one in each disc) and will accordingly be forced by the spring 148 or 149 into the notches, it being understood by those skilled in the art that only one such alignment of the notches can occur at any one time. As the code disc position corresponds to the electrica-l code impulses received over the line 32. the code of impulses which has been received is indicated by the identity of the selected index pin. The particular index pin selected also indicates the subsequent operation to take placesuch as printing, spacing or case shifting.

The operation of the transferring and indexing mechanism is as follows: At a moment in the cycle of operation of the printer at or about the time that the last selector liver 95 is being positioned that portion of t e will pass under the cam follower 63,-permitt ng the trip bail 62 to operate and to release the driven disc 124 to start rotating, as shown in Figure 24. The friction clutch 44 through lug 125 and pin 127 drives the main cam 119 through a small angle, turning also the sleeve 132 (see Figure 9). The crown cam 134 moves from under the abutment 135 and the spring 133 forces the sleeve 132 into the teeth of the clutch member 131 thus coupling the main cam 119 positively to the main shaft 24., In this manner, the main cam 1191s started gently by power through-the friction clutch 44, and after a short initial movement,

' driven disc 57 which is of reduced radius it is directlyand positively coupled to the driving shaft 24 through toothed connections. Thus the advantage of a positive toothed clutch connection for the transfer power is obtained while at the same time the shock or jar as well as noise due to sudden starting by engagement of the teeth of such a clutch is obviated through the use of the friction clutch 44. I

As the main cam 119 rotates further, the transfer bail roller 138 rides in the groove 120 and rocks the bail 117. The transfer levers 112 are carried downward toward the previously positioned selector levers 95 and almost immediately any transfer lever 112 which is to be changed will engage an abutment of a selector lever 95 with one of its arms 113 or 114 depending. on the setting of the lever 95 in accordance with the previously received code combinations of impulse conditions, it being understood thatby this time all of the levers have been positioned in accordance with the received code combinations as the transfer bail carries the specific transfer lever further, the fixed abutment acts as a pivot or fulcrum for the transfer lever 112, to rock the transfer lever 112 about the pivot shaft 116. As the transfer lever 112 rocks upon the pivot ,shaft 116 its head 115 in the slot 141 of theassociated selector disc 139 shifts the latter-into its new position to correspond to. the positive or negative nature of the signal received from the line 32. Should the code disc 139 be already in the position corresponding to the position, of the associated selector lever 95, (the abutment presented to the transfer lever will not'be engaged, the transfer lever will not be rotated upon the pivot shaft 116 and the code disc 139 will not be shifted. Thus by one movement of the transfer bail 117 the setting of the five selector levers 95 will be transferred simultaneously through'the five transfer levers 112 to the five code discs 139 and-a new specific index pin 143 will move to its operated posit on, the prior operated index pin 143-being llfted into non-operated position by the cam action of the edges of the notches in the one or more discs 139 which have been moved in the' action of transferring.

As the maincam 119 rotates further, the

transfer levers'112 will be lifted from the selector levers 95 so that the latter maybe positioned in accordance with thesucceeding code combination of impulses while printing operations in accordance with the setting of dlscs 139 takes place. As the main cam 119 .reaches the end of its revolution the crown cam 134 again engages the fixed abutment 135 forcing the sleeve 132 to the left-to disengage the same from the/toothed member 131. The frictlon clutch 44 continues to drive the main cam 119 for the small remainder of the revolution until it is stopped by the lug 125 on the driven disc 124 engaging the end 128 of the trip bail 62, as shown in Figure 10.

Typewheel angular adjustment also drives 3. gm? 152 which, it will be noted,

is of smaller diameter than gear 40 and accordingly rotates at a greater speed than gear 40. The ear 152 constitutes the driving element 0 a third friction clutch 153. The friction clutch 153 is similar in construction to the friction clutches 50 and 44 but the power is transmitted through clutch 153 in reversed direction, the median disc or gear 152 being the driving member and the sleeve-and-fiange element 154 being the driven member. The member 154 is fixed to a stop shaft 155 by means of a pin 156. The stop shaft 155 is mounted in the bearing journals 157 and 158 and is positioned on the axis of the cylindrical assembly of the index index pin 151 which happens to be in selected position and therefore nearerto the axis of I the assembly (see'Figure'13). When the stop arm 159 en ages the selected pin 151, the stop arm is brought to a sudden stop. In order to prevent rebound when the rotating stop arm 159 is brought suddenly to a stop by engagement with the selected pin 151, the stop arm carries a latch 160 which passes over the end of the selected pin 151 and engages with the opposite side thereof. The latch 160 is mounted pivotally upon the index arm 159 by a pin 161 and is retained in position by 'a sprlng 162. The free end of the latch 160 has a cam surface 163 (Figure 14) by means of which, the latch 160 rides over the ends of the index pins 143. It will be evidentfrom this description that the motor 25 drives the stop shaft 155 frictionally except when the stop shaft 155 is restrained against rotation by the index arm 159 coming into engagement with a selected index pin. a

The stop -shaft 155 has slidably mounted thereon a bevel gear 164 as shown in Figure 17. The stop shaft is square in cross section so-that when it rotates the bevel gear 164 rotates with it, but thebevel gear 164 may slide longitudinally along the shaft 155. In mesh with the bevel gear 164 is a bevel gear 165 which has a hub 166 integral therewith. The driving bevel gear 164 is held in mesh with the driven gear 165 by an izo a sleeve and is journalled in a bearing 171 mounted in the typewheel carriage 172. The typewheel carriage 17 2 comprises a base casting 173 and a top plate 174 connected by vertical struts, not shown. The top plate 174 carries a top journal member 17 5. Slidably mounted in the sleeve 166 and in the top journal member 175 is a vertical shaft 176. The sleeve hub 166 is held in axial alignment by co-operative action of the shaft 176 and the top journal member 17 5. The vertical shaft 176 carries a type wheel 177 and turns with the bevel gear 165. An arm 178 is secured to the vertical shaft 176 and engages within the forked end of an arm 179 secured to the sleeve hub 166. This provides a means for preventing rotation of the shaft 17 6 with respectto the sleeve 166.

The typewheel 177 carries a plurality of type which are presented to the surface of t e paper 180 in a manner to be described hereinafter. The angular adjustment of the typewheel 177 is effected in the following manner: After the index arm 159 has been latched in engagement with the selected index pin the selector discs 139 are shifted in response to a subsequently incoming code combination of impulses. The shifting movement of the selector discs 139 lifts the selected index pin and selects another index pin in accordance with incoming code combination of impulses. The return to normal of the previously selected index pin releases the index arm 159 and thereby releases the stop shaft 155. The motor 25 acting through the friction clutch 153 then turns the shaft 155, the arm 159 and the typewheel 177 until the index arm 159 engages the newly se lected index pin. This arrests the index arm 159, stop shaft 155 and ty ewheel 177, thus adjusting the typewheel 1 7 to present the selected type to the paper 180 if a character is to be printed or ad usting the stop shaft 155 to a position corresponding to an oper-' ation other than the printing of a character.

It will be evident from the preceding description that the friction clutch 153 continually urges the typewheel 177 to rotate and that the typewheel rotates except when restrained by the stop mechanism controlled by the selected index pin, the typewheel then being stopped in the angular position corresponding to the selected pin.

. Printing Operating in the cam groove 120 of-the main cam 119 (Figure 17) is the roller 181 of a rinting bail 182 pivoted on a shaft 183. As sfiown in Figure 20, the bail 182 has extending therefrom an operating arm 184 which carries a pin 185. The pin 185 extends through a slot 186 in one end of a linkfl 187, which, at its other end, is pivotally connected as by means of a screw 188 to an arm 189 of a bell crank 190. The bell crank 190 is fixed to a shaft 191 which is j ournaled in the frame of the printer and extends across the width of the paper sheet 180. Secured to the arm 192 of bell crank 1'90 and to a similar arm 192 (Figure 17 on the shaft 191 is the platen bar 193 which extends across the width of the paper 180, behind the paper, and in position to press the paper throughout the entire line of printing toward the typewheel 177 so that the type character which is pre- Sented to the paper will be printed upon the paper regardless of the position of the typewheel along the line of printing when the platen bar 193 is operateds A platen spring 194 extends from a stud 195 on the bell crank arm 189 to a fixed point (not shown) on the excess movement ofthe operating arm 184.

The link 187 has two lugs 196 which form a yoke to span the head 197 of the arm 198 of a bell crank 199 pivoted to the frame of the printer at 200. The bell crank 199 has an operating arm 201 which has pivoted thereto at 202 a push link 203. The other end 204 of the push link 203 is forked and spans a pin 205 on an arm 206 rigidly secured to a square typelock shaft 207. A spring 208 has one end secured to the frame of the printer and the other end secured to the arm 206 at a point 209 and tends to rock the shaft 207 in a direc tion to cause the pin 205 to push against the push link 203.

Square shaft 207 has secured thereto a type lock flange 210 as shown in Figure 17. A typelock dog 211 is pivoted at 212 upon the typewheel carriage 172 and moves with the carriage. The dog 211 has a pair of jaws 213 which at all times span the typelock flange 210 regardless of the ositi'on of the carriage 172, the flange 210. eing made 'of sufficient length for this purpose. The typelock dog 211 is provided with an operating arm 214 (Figure 18) which is adapted to engage within any one of a plurality of notches 215 in the periphery of a typelock wheel 216 which is fixed to the hub 166 of the bevel gear 165. The wheel 216 turns with the typewheel 177 and when the latter comes to a stop the operating arm 214 of the typelock dog 211 may engage within a notch 215 to lock the typewheel in printing position.

When the operating arm 214 of the typelock dog 211 engages within a notch 215 to lock the typewheel in printing position, the selected type character on the printing wheel 177 is accuratel centered so that a proper impression will be made upon the paper.

In 0 ration, the cam groove 120 depresses the printing bail 182 quickl raising the operating arm 184 thereof. the arm 184 is raised the spring 194 rocks the bell crank 190 counter-clockwise as viewed in Figure and the platen 193 presses the paper 180 against the selected type character on the typewheel 177 to perform the printing operation. During the rocking movement of the bell crank 190 the link 187 with the head 197 on the arm 198 of the bell crank 199 rocks the bell crank 199 about its pivot 200, counterclockwise as viewed in Fi re 20, and draws the link 203downward t ereby permitting the sprin 208 to rock the typelock shaft 207 in a 0100 wise direction. As the shaft 207 rocks clockwise it operates through the type lock flange 210 (Figure 17) to rock the typelock dog 211 counterclockwise causing the operating arm 214 of the dog 211 to enter the notch 215 b the tension of the spring 208 and the t pew eel 177 is held locked during the peri of the printing impression.

The typewheel 177 is inked by the inking wheel 217 (Fig. 1) mounted upon an arm 218 pivoted at 219 and pressed against the typewheel by a spring 220.

Thus, printing is effected by the cam groove 120 of the main cam 119 operating the cam follower roller 181 on the printing bail 182 and the latter in turn operating the platen 193 through a mechanical'linkage to press the paper 180 against the t wheel 177, the centering and locking of t e type t e same time.

character to be printed taking place at Letter spacing The carriage 172 has extending horizontally therefrom two front studs 221 (Figure 1) carrying the front wheels 222 and a rear stud 221 (Figure 17) carrying a rear wheel 222'. -The front wheels 222 rest on-a rail 223 and the rear wheel 222 rests on a rail 223'. The carriage is adapted. to be moved along the rails step by step by a spacin mechanism which comprises a toothed rac 224 (see Figure 3) carried by the forwardly extending studs 221, a holding pawl 225 and a driving pawl 226. The holding pawl 225 is pivoted intermediate its ends at a point 227 fixed to the frame, of the machine and has a'pendant" latch 228 pivoted thereto at -229. The latch 228'engages 'a latch plate 229 fixed to a rocker shaft 230.

A spring 231 has one of its ends connected to the pawl 225 at 232 and its other end connected to a stationary point 233 on the frame and continually maintains the end 234 of the pawl 225 in engageinentwith the teeth in the rack 224. The driving pawl 226. is pivoted intermediate its ends' on a screw 235 fixed to the end of arm 236 of a bell crank I 237 and has a pendant latch 238 pivotally connected thereto at 239. The pendant latch 238 also engages the latch plate 229. A spring 240 has one end connected with the pawl 226 at 241 and its other end-is connected to a stud 242 on the arm 236 of the bell crank 237 and continually maintains the end 243 of the pawl 226 in engagement with the teeth of the rack 224.

The bell crank 237 is pivoted to the frame of the printer at 244 and is constantly urged to rock in a counterclockwise direction by a spring 245 one end of which is fixed to the arm 236 of the bell crank 237 at 246 and the other end of which is attached to a fixed point 247 on the frame. The horizontal arm 248 of the bell crank 237 engages the space and shift bail 249. The bail 249 is pivoted to the frame of the printer at 250 (Figure 17) and carries a cam follower roller 251 which rides upon the cam edge 121 of the main cam 119. Just prior to the time of transfer of the setting of the selector levers 95 to the discs 139 the main cam 119 permits the roller 251 to drop. The spring 245 then rocks the bell crank 237 counterclockwise (as viewed in Figure 3) and the driving pawl 226 is carried bodily towards the left, a distance sufficient to bring the end 243 thereof 225 then eitgages the next tooth in the rack 224 and hol s the carriage 172 in its advanced position. In this manner, the typewheel car- ."riage 172 is moved along the rail 223 step by step carrying the typewheel 177 along the line of printing and stopping in each printing position along the line of printing. To effect the s acing between words in a line, a part of t e peri hery of the typewheel having no type. character thereon is presented to the paper and the same operations take place as in printing a character, thus effecting a spacing without printing.

Case shift The letters of the alphabet are arranged in the up r row of type faces and are printed when t e type wheel 177 is in the lower position as shown in solid lines in Figure 17. The numerals and the other characters are arranged in the lower row of type faces and are printed when the typewheel 17 7 is in the upper position as shown in dotted lines in F1 re 17. v

v previously described, there are six selector levers 95 and five of these are effective 

